JP3214311B2 - Air conditioner - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method for controlling the number of revolutions of a compressor of a refrigeration cycle in accordance with a deviation between a predetermined target indoor temperature and the temperature of air blown into a room. The present invention relates to an air conditioner configured to adjust a temperature.

[0002]

2. Description of the Related Art As a prior art of such an air conditioner, there is one disclosed in Japanese Patent Application Laid-Open No. 6-174291. According to this, for example, when the set outlet air temperature of the indoor heat exchanger and the outlet air temperature are both stable at T0 and the set outlet air temperature is changed to Ts,
If the absolute value of the deviation (| Ts-T0 |) between the deviation and T0 is larger than a predetermined value, the amount of increase or decrease of the compressor rotation speed is determined in accordance with this deviation (| Ts-T0 |). By changing the rotation speed of the compressor, the temperature of the blown air is made to approach the set blown air temperature Ts.

[0003]

However, in the case of the prior art, the amount of increase or decrease in the number of rotations of the compressor is determined by the difference (| Ts -T0 regardless of the amount of air passing through the indoor heat exchanger.
Since the decision is made only according to |), the following problem occurs. For example, using an evaporator of a refrigeration cycle as an indoor heat exchanger, an air conditioner that performs indoor cooling with this evaporator, or a condenser of a refrigeration cycle as an indoor heat exchanger,
In the air conditioner that performs indoor heating with this condenser, when the compressor rotation speed is changed by the above-mentioned increase or decrease determined in accordance with the above-mentioned deviation (| Ts-T0 |), the indoor heat exchanger passes at this time. Since the air volume was the predetermined air volume, the way the outlet air temperature approaches the set outlet air temperature Ts is shown in FIG.
It is assumed that it is optimal as shown by the solid line in FIG.

[0004] Fig. 22A shows the behavior of the temperature of the blown air at the time of the indoor cooling, and Fig. 23A shows the behavior of the temperature of the blown air at the time of the indoor heating. However, when the amount of air passing through the indoor heat exchanger at this time is larger than the predetermined amount of air, the evaporator or the condenser has insufficient cooling capacity or insufficient heating capacity compared to when the amount of air passing through the indoor heat exchanger is the predetermined amount of air. As a result, the speed at which the blow-off air temperature approaches the set blow-out air temperature Ts is reduced as shown in FIG.
2 (a), as shown by the one-dot chain line in FIG.

[0005] Conversely, if the amount of air passing through the indoor heat exchanger at this time is smaller than the predetermined amount of air, the evaporator or the condenser has an excessive capacity compared to when the amount of air passing through the indoor heat exchanger is the above predetermined amount of air. Therefore, the speed at which the blown air temperature approaches the set blown air temperature Ts increases, but the rate of temperature change is too large, causing overshoot as shown by the broken lines in FIGS. 22 (a) and 23 (a). I will.

FIGS. 22 (b) and 23 (b) show the behavior of the number of revolutions of the compressor corresponding to the cases of FIGS. 22 (a) and 23 (b). In view of the above, an object of the present invention is to make the temperature of air blown into a room always approach a predetermined target room temperature in an optimal state regardless of the amount of air passing through the indoor heat exchanger. .

[0007]

SUMMARY OF THE INVENTION To achieve the above object, according to the invention of claim 1, an air blowing means for generating an air flow (4), this
Air passage for guiding the air generated by the air blowing means (4) into the room
(2) and when driven by the driving means (37)
A compressor (25) for sucking, compressing, and discharging a refrigerant;
Condenser (26) for condensing the refrigerant from the compressor (25),
Means (2) for reducing the pressure of the refrigerant from the condenser (26)
7) and the refrigerant from the pressure reducing means (27) is evaporated.
And an evaporator provided in the air passage (2).
Refrigeration cycle (24) with (22) and predetermined target
The deviation between the room temperature and the temperature of the air
The target rotation of the compressor (25) according to the rate of change of the deviation
Means for determining the number of revolutions (steps 140 to 1)
90), and the actual compressor speed is equal to the target speed.
Drive control means for controlling the drive means (37) so that
A control device (39) having a step (step 200).
The air that has passed through the evaporator (22) is blown into the room.
By doing so, it is configured to perform indoor cooling
As the amount of air passing through the evaporator (22) increases,
The target rotational speed determining means (steps 140 to 19)
Increasing said target speed determined by 0)
It is characterized by . According to the second aspect of the present invention,
The temperature setting means (4) operated by the air conditioning driver
8) and the degree of air cooling in the evaporator (22)
Cooling degree detecting means (40) for detecting
The room temperature is set by the temperature setting means (48).
The temperature of the air blown into the room,
A temperature indicating a degree of air cooling in the generator (22) . According to the third aspect of the present invention, the air flow
Blower means (4) for generating air, and the blower means (4)
Air passage (2) for guiding the generated air into the room, and driving means
Suctioning and compressing the refrigerant when driven by (37);
A compressor (25) for discharging, and a cooler from the compressor (25).
A medium is condensed and provided in the air passage (2).
Condenser (23), and the refrigerant from the condenser (23)
A pressure reducing means (28) for reducing the pressure;
8) A chiller equipped with an evaporator (26) for evaporating the refrigerant from
Freezing cycle (24), predetermined target indoor temperature and indoor
Depending on the deviation from the outlet air temperature and the rate of change of this deviation
A target number of revolutions for determining a target number of revolutions of the compressor (25).
Turn number determining means (steps 220 to 260, 190);
And the actual compressor speed is the target speed.
Drive control means (step) for controlling the drive means (37)
A control device (39) comprising a control unit (200).
By blowing the air passing through the compressor (23) into the room.
What, it is configured to perform the room heating, the condenser
As the amount of air passing through the vessel (23) increases,
Target rotation speed determining means (steps 220 to 260, 190)
The target rotation speed determined by
Sign . According to the fourth aspect of the present invention, an air flow is generated.
Blower means (4) and the air generated by the blower means (4)
The air passage (2) for guiding the air into the room and the driving means (37)
Therefore, the pressure at which the refrigerant is sucked, compressed, and discharged when driven
The compressor (25) condenses the refrigerant from the compressor (25).
And a condenser provided in the air passage (2).
(23) The pressure of the refrigerant from the condenser (23) is reduced.
Pressure means (28), and cooling from the pressure reducing means (28).
Refrigeration cycle provided with an evaporator (26) for evaporating a medium
(24) and temperature setting means operated by the air conditioning driver
(48) and the high pressure of the refrigeration cycle (24) are detected.
High-pressure pressure detecting means (42) for outputting the pressure, and the temperature setting means
Target high pressure determined according to the setting position of (48)
And the high pressure detected by the high pressure detecting means (42).
Depending on the deviation from pressure and pressure and the rate of change of this deviation,
A target rotation speed for determining a target rotation speed of the compressor (25);
Determining means (steps 220 to 260, 190) and actual
The drive speed is set so that the compressor speed at that time becomes the target speed.
Drive control means for controlling the moving means (37) (step 20)
A control device (39) comprising:
By blowing the air passing through (23) into the room
And the condenser is configured to perform indoor heating .
(23) As the air volume passing through increases, the target
In the rotation speed determining means (steps 220 to 260, 190)
Characterized in that the target rotation speed determined by
And According to the fifth aspect of the present invention, an air flow is generated.
Air blowing means (4) and air generated by the air blowing means (4)
(37) and an air passage (2) for guiding the air into the room.
Compression that draws, compresses, and discharges refrigerant when driven
(25) condensing the refrigerant from the compressor (25)
Condenser (49c), refrigerant from the condenser (49c)
Pressure reducing means (28) for reducing the pressure of
8) A chiller equipped with an evaporator (26) for evaporating the refrigerant from
Freezing cycle (24) and refrigerant in the condenser (49c)
Refrigerant-water heat exchange, which exchanges heat with the warm water flowing inside itself
Exchanger (49) and the refrigerant / water heat exchanger (49)
Hot water flows through the inside and into the air passage (2)
Hot water circuit provided with hot water heat exchanger (50) provided
(54), predetermined target indoor temperature and indoor air temperature
Pressure, and the rate of change of this deviation.
Target rotation speed determining means for determining the target rotation speed of the compressor (25)
Steps (steps 215 to 260, 190) and the actual
The drive mechanism is operated so that the compressor speed becomes the target speed.
Drive control means for controlling the step (37) (step 200)
And a controller (39) comprising:
By blowing the air passing through the vessel (50) into the room.
The heating water in the room.
As the volume of air passing through the heat exchanger (50) increases
The target rotation speed determining means (steps 215 to 26)
0, 190) to increase the target rotational speed.
It is characterized by doing. In the invention according to claim 6, the contract
Claim 5: The temperature setting operated by the air conditioning driver.
Means (48) and flows into said hot water heat exchanger (50)
Hot water temperature detecting means (58) for detecting the hot water temperature
The target room temperature is provided by the temperature setting means (48).
Is the target hot water temperature set by
The outlet air temperature flows into the hot water heat exchanger (50).
It is characterized by a hot water temperature .

[0008] According to this, in both the case of performing indoor cooling and the case of performing indoor heating, when the amount of air passing through the indoor heat exchanger is large, the number of rotations of the compressor becomes higher, and conversely, the air passes through the indoor heat exchanger. When the air volume is small, the compressor rotation speed becomes low.
Therefore, the temperature of the air that has passed through the indoor heat exchanger is almost constant regardless of the air volume that passes through the indoor heat exchanger. Approach.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, a first embodiment in which the present invention is applied to an air conditioner for an electric vehicle will be described with reference to FIGS. First, the overall configuration of the present embodiment will be described with reference to FIG. The indoor unit 1 includes a duct 2 as an air passage for guiding air into the vehicle interior. Inside and outside air switching means 3 and blowing means 4
Is connected.

The inside / outside air switching means 3 includes an inside air suction port 5 and an outside air suction port 6 formed on the upstream side of the duct 2, and an inside / outside air switching door 7 for selectively opening and closing these suction ports 5, 6.
And The inside / outside air switching door 7 is driven by a servo motor (not shown). The blower 4 includes a fan case 8, a fan 9, and a fan motor 10. The fan motor 10 is rotated by driving a fan 9 by being energized from a battery (not shown) which is a DC power supply, and blows inside air or outside air into the vehicle interior through the duct 2.

At the downstream end of the duct 2, there is provided a center face outlet 11 for blowing out the air passing through the duct 2 from the front center of the passenger compartment toward the upper body of the occupant. A side face outlet 12 that blows out toward the upper body or side glass, a foot outlet 13 that blows out the air toward the occupant's feet, and a defroster outlet 14 that blows out the air toward the inner surface of the window glass are formed. ing.

A center face door 18 for adjusting an air flow rate to each of the air outlets is provided at each upstream portion of the air passages 15 to 17 communicating with the center face air outlet 11, the foot air outlet 13, and the defroster air outlet 14. , A foot door 19 and a defroster door 20 are provided. The center face air outlet 11 and the side face air outlet 12 are provided with an occupant opening / closing door 21 for manually adjusting the air blowing amount according to the occupant's preference.

Inside the duct 2, a cooling indoor heat exchanger 22 and a heating indoor heat exchanger 23 for exchanging heat between the refrigerant flowing inside the duct 2 and the air inside the duct 2 are provided on the entire surface of the duct 2. Have been. Each of these heat exchangers 22 and 23 is a heat exchanger forming a part of a refrigeration cycle 24 described later, and the heat exchanger 22 functions as an evaporator in a cooling mode described later. It functions as a condenser in a heating mode described later.

The refrigeration cycle 24 is a heat pump type refrigeration cycle for cooling and heating the interior of the passenger compartment by the indoor heat exchanger 22 for cooling and the indoor heat exchanger 23 for heating. , Compressor 25, outdoor heat exchanger 2
6. A cooling decompression device 27, a heating decompression device 28, an accumulator 29, and a four-way valve 30 for switching the flow direction of the refrigerant are provided. In the figures, 32 and 33 are solenoid valves, 34 and 35 are one-way valves, and 36 is an outdoor fan.

The compressor 25 sucks, compresses, and discharges refrigerant when driven by the electric motor 37. The electric motor 37 is disposed integrally with the compressor 25 in a sealed case, and the rotation speed continuously changes by being controlled by the inverter 38. The control of the inverter 38 is controlled by a controller 39.

As shown in FIG. 2, the controller 39 includes a degree of air cooling in the cooling indoor heat exchanger 22 (specifically, an air temperature immediately after passing through the heat exchanger 22).
And signals from a post-passing air temperature sensor 40 for detecting the pressure, a compressor speed sensor 41 for detecting the speed of the compressor 25, and a high pressure sensor 42 for detecting the high pressure of the refrigeration cycle. Each signal from each lever and switch at 43 is also input.

As shown in FIG. 3, the control panel 43 has an air outlet mode setting lever 44 for setting each air outlet mode, an air volume setting lever 45 for setting the air volume blown into the vehicle interior, and an inside / outside air switching mode. Inside / outside air switching lever 46, a cooling switch 47a for setting the refrigeration cycle 24 to the cooling mode, and a heating switch 47b for setting the heating mode to the heating mode
And a temperature setting lever 48 for setting a vehicle interior target temperature.

There are specifically five setting modes by the air volume setting lever 45, and four modes for driving the fan 9 (Lo, Me1, Me2, Hi) in addition to the mode for stopping the fan 9 (OFF). There is. Needless to say, the rotation speed of the fan 9 for the setting mode of the air volume setting lever 45 is Lo <Me1 <Me2 <Hi.

The cooling switch 47a and the heating switch 47b are configured not to be turned on at the same time. And, the cooling switch 47a and the heating switch 47b
Can be turned off at the same time by lightly pressing one of the switches 47a and 47b while the other is on. In this case, the air blow mode in which the compressor 25 stops is instructed.

A sliding terminal (not shown) is connected to the temperature setting lever 48.
3 is moved in the left-right direction in FIG. 3 so that the sliding terminal slides on a resistance element to which a predetermined voltage is applied to both ends. The control device 39 reads the voltage output from the sliding terminal to read the set position of the temperature setting lever 48.

A well-known microcomputer including a CPU, a ROM, a RAM, and the like (not shown) is provided inside the control device 39. The signals from the sensors 40 to 42 and the signals from the control panel 43 are The data is input to the microcomputer via an input circuit (not shown) in the control device 39. Then, the microcomputer executes processing described later, and controls each electric driving means such as the inverter 38 based on the processing result.
The control device 39 is supplied with power from a battery (not shown) when a key switch (not shown) of the vehicle is turned on.

When the cooling switch 47a is turned on by an occupant in the vehicle, the microcomputer controls the four-way valve 30 and the solenoid valve 32, and the refrigeration cycle 24 enters the cooling mode. The flow of the refrigerant in the cooling mode is as follows: the compressor 25 → the four-way valve 30 → the outdoor heat exchanger 2
6 → cooling decompression device 27 → cooling indoor heat exchanger 22 → accumulator 29 → compressor 25.

When the heating switch 47b is turned on by an occupant in the vehicle, the microcomputer controls the four-way valve 30, the solenoid valves 32 and 33, and the refrigeration cycle 24 enters the heating mode. The flow of the refrigerant in the heating mode is as follows: the compressor 25 → the four-way valve 30 → the indoor heat exchanger 23 for heating → the decompression device 28 for heating → the outdoor heat exchanger 26 →
The order is accumulator 29 → compressor 25.

Next, control processing of the inverter 38 performed by the microcomputer will be described with reference to the flowchart of FIG. First, in step 110, the RAM inside the microcomputer is initialized. Then, in the next step 120, each of the sensors 4
Signals from 0 to 42 and signals from each lever and switch of the control panel 43 are read.

Then, in the next step 130, it is determined whether or not the cooling switch 47a is turned on. If the determination here is YES, then in the next step 140, from the characteristic of FIG. 5 stored in the ROM, depending on the position of the temperature setting lever 48, immediately after passing through the cooling indoor heat exchanger 22, Determine the target air temperature TEO. here,
The target temperature TEO is determined to be 3 (° C.) when the temperature setting lever 48 is at the left end in FIG. 3, and is determined to be 20 (° C.) when the temperature setting lever 48 is at the right end in FIG.

In the next step 150, the deviation En between the target temperature TEO and the actual air temperature TE detected by the post-passing air temperature sensor 40 is calculated based on the following equation (1).

[0027]

## EQU1 ## In the next step 160, the deviation change rate Edot is calculated based on the following equation (2).

[0028]

## EQU2 ## Since En is updated every 4 seconds, En-1 is equal to En-dot.
Is 4 seconds before. Next, at step 170, based on the membership functions of FIG. 6 and the rules of FIG.
Target increase / decrease rotational speed Δ at En and Edot calculated by
Calculate fz (rpm). Here, this target increase / decrease rotational speed Δfz
Is the number of revolutions of the compressor 25 that increases or decreases from the target number of revolutions fn-1 (rpm) four seconds ago.

More specifically, an input fitness CF is calculated from CF1 determined in FIG. 6A and CF2 determined in FIG. 6B based on the following equation (3). Δfz is calculated based on the following equation 4 from the rule value of

[0030]

## EQU3 ## CF = CF1 × CF2

[0031]

Δfz = Σ (CF × rule value) / ΣCF Then, in the next step 180, as shown in FIG.
The correction target increase / decrease rotational speed Δf is calculated by multiplying the target increase / decrease rotational speed Δfz by a coefficient different according to the setting position of the air volume setting lever 45. In the present embodiment, the coefficient in FIG. 8 is determined by the correction target increase / decrease rotational speed Δf as the rotational speed of the fan 9 increases (as the air flow passing through the cooling indoor heat exchanger 22 increases). Is set to be large.

Then, in the next step 190, the target rotational speed fn of the compressor 25 is calculated based on the following equation (5).

[0033]

Fn = fn-1 + .DELTA.f In the next step 200, the current input to the inverter 38 is set so that the compressor speed detected by the compressor speed sensor 41 becomes the target speed fn. Control.
Then, the process returns to step 120.

On the other hand, if the determination in step 130 is NO, the process proceeds to step 210 where the heating switch 47b
It is determined whether or not is turned on. If YES is determined here, the target high pressure PCO is determined at step 220 according to the position of the temperature setting lever 48 from the characteristics of FIG. 9 stored in the ROM. Here, this target high pressure PCO is determined to be 8 (kg / cm ² G) when the temperature setting lever 48 is at the left end in FIG. 3, and is 16 when the temperature setting lever 48 is at the right end in FIG.
(Kg / cm ² G).

In the next step 230, the deviation Dn between the target high pressure PCO and the actual high pressure PC detected by the discharge pressure sensor 42 is calculated based on the following equation (6).

[0036]

Dn = PCO-PC Then, in the next step 240, the deviation change rate Ddot is calculated based on the following equation (7).

[0037]

Ddot = Dn-Dn-1 Here, Dn is updated every four seconds, so that Dn-1 is a value four seconds before Dn. Next, step 250
At step 230, based on the membership function of FIG. 10 and the rules of FIG.
The target increase / decrease rotational speed Δfz (rpm) at Dn and Ddot calculated at 240 is calculated. The method of calculating the target increase / decrease rotational speed Δfz in step 250 is the same as that in step 170
Therefore, the description is omitted.

Then, in the next step 260, as in the case of step 180, as shown in FIG. 8, the correction is carried out by multiplying the target increase / decrease rotational speed Δfz by a coefficient different according to the set position of the air volume setting lever 45. The target increase / decrease rotational speed Δf is calculated. Then, in steps 190 and 200
After performing the processing in (1), the processing returns to the processing in step 120.

If it is determined in step 210 that the heating switch 47b has not been turned on, the operation of the compressor 25 is stopped in step 270 to set the air blow mode. Here, a specific calculation example of the target rotation speed fn will be described. For example, when Dn = 6.25 in the heating mode,
From FIG. 6A, CF1 is NB = 0, NS = 0, ZO =
0, PS = 0.75 and PB = 0.25. Also, D
When dot = −0.15, NB = 0 and N from FIG.
S = 0.5, ZO = 0.5, PS = 0, and PB = 0.

Therefore, the denominator of the above equation (4), ie, {CF}
Is 0.75 × 0.5 + 0.75 × 0.5 + 0.25 ×
0.5 + 0.25 × 0.5 = 1. Further, 分子 (CF × rule value) which is a numerator of the above formula 4 is 0.75 ×
0.5 × 0 + 0.75 × 0.5 × 100 + 0.25 ×
0.5 × 300 + 0.25 × 0.5 × 600 = 150. Thus, Δfz = 150.

If the set position of the air volume setting lever 45 at this time is Me2, as can be seen from FIG.
= 125. Therefore, the compressor speed fn is increased by 125 (rpm) from the speed fn-1 four seconds before. When ΣCF = 0, Δf = 0. As described above, by controlling the energization of the inverter 38, in the cooling mode, the air temperature immediately after passing through the cooling indoor heat exchanger 22 approaches the target temperature TEO, and the temperature of the air blown into the vehicle interior is reduced by the temperature setting lever. 48 approaches the target temperature set. In the heating mode, the high pressure approaches the target high pressure PCO, and the temperature of the air blown into the vehicle interior approaches the target temperature set by the temperature setting lever 48.

The above steps constitute means for realizing the respective functions. Next, a specific operation when the cooling mode is set by the cooling switch 47a and the target temperature TEO is lower than the actual temperature TE when the air conditioner is started (time t = 0) will be described with reference to FIG. . In this case, in the initial stage of starting the air conditioner, the compressor speed must be increased to increase the cooling capacity.
And Δf are both calculated as positive values, and the compressor rotation speed increases.
As shown in (b), the air volume set by the air volume setting lever 45 increases as the air volume increases.

Therefore, the temperature of the air that has passed through the cooling indoor heat exchanger 22 is always substantially constant, regardless of the air volume. Therefore, how the temperature of the air blown into the vehicle compartment approaches the target temperature set by the temperature setting lever 48 is shown in FIG.
As shown in (a), the air temperature TE that has passed through the cooling heat exchanger 22 always becomes optimal in the same manner as approaching the target temperature TEO.

The specific operation when the heating mode is set by the heating switch 47b and the target high-pressure PCO is higher than the actual high-pressure PC when the air conditioner is started (time t = 0) will be described with reference to FIG. explain. In this case, since the compressor speed must be increased to increase the heating capacity in the initial stage of the air conditioner startup, both Δfz and Δf are calculated as positive values, and the compressor speed increases. As shown in FIG. 13B, the degree of this increase increases as the air volume set by the air volume setting lever 45 increases.

Therefore, the temperature of the air that has passed through the heating indoor heat exchanger 23 is almost always constant irrespective of the magnitude of the air volume. Therefore, how the temperature of the air blown into the vehicle compartment approaches the target temperature set by the temperature setting lever 48 is shown in FIG.
Target high pressure PCO of actual high pressure PC as shown in (a)
It will always be optimal as well as approaching. As described above, in the present embodiment, the target increase / decrease rotational speed Δfz is calculated in accordance with the deviation between the predetermined target vehicle interior temperature and the temperature of the air blown into the vehicle interior, and further passes through the indoor heat exchanger. The correction target increase / decrease rotational speed Δf is calculated so that the target increase / decrease rotational speed Δfz increases as the amount of air to be increased increases. The blow-out air temperature always approaches a predetermined target vehicle interior temperature in an optimal state.

Next, a second embodiment of the present invention will be described with reference to FIGS. Note that the same reference numerals as in the first embodiment denote the same parts as in the first embodiment, and a description thereof will be omitted. In the present embodiment, the coolant / water heat exchanger 49, the heater core 50, the hot water tank 51,
And a hot water circuit 54 connected to the water pump 52 by a hot water pipe 53.

The refrigerant water heat exchanger 49 is formed by meandering and bending a hollow cylindrical pipe 49a made of an aluminum alloy. An internal passage 49b of the pipe 49a is connected to the hot water pipe 53, and a plurality of passages 49c formed in a thick portion of the pipe 49a.
Is connected to the refrigerant pipe 31. Therefore, the passage 4
9b functions as a hot water passage through which hot water flows in the hot water circuit 54, and the passage 49c functions as a refrigerant passage through which the refrigerant in the refrigeration cycle 24 flows.

Further, the heater core 50 is provided at the portion where the indoor heating heat exchanger 23 (FIG. 1) is provided in the first embodiment. This is a hot water heat exchanger that exchanges heat with the air in the duct 2. As described above, the hot water flows in the passage 49b and the refrigerant flows in the passage 49c, so that the hot water and the refrigerant exchange heat in the refrigerant water heat exchanger 49.
Then, the refrigerant in the refrigeration cycle 24 is condensed in the passage 49c. That is, the passage 49c functions as a condenser. Then, the hot water in the hot water circuit 54 is heated in the passage 49b.

Although not shown in FIG. 14, the compressor 25 is similar to the first embodiment.
The motor is driven by an unillustrated electric motor (same as the electric motor 37 in FIG. 1) disposed in a sealed case integrally with the motor, and is controlled by an unillustrated inverter, so that the rotation speed continuously changes. This inverter is energized by the control device 39 (FIG. 16).

As shown in FIG. 16, the control device 39 includes the following levers of the post-passing air temperature sensor 40, the compressor speed sensor 41, and the control panel 43.
In addition to the signals from the switches, an inside air temperature sensor 55 for detecting the inside air temperature in the vehicle interior, an outside air temperature sensor 56 for detecting the outside air temperature, a solar radiation sensor 57 for detecting the amount of solar radiation applied to the vehicle interior, and a heater core 50 Each signal is input from a water temperature sensor 58 that detects the temperature of the hot water flowing into the inside.

Next, the control process of the inverter performed by the microcomputer in the control device 39 will be described with reference to FIG.
A description will be given based on the flowchart of FIG. Here, only the parts different from the first embodiment will be described. Further, the control device 39 determines that the flow of the refrigerant in the refrigeration cycle 24 in the heating mode is the compressor 25 → the refrigerant water heat exchanger 49 → the heating depressurizing device 28 → the outdoor heat exchanger 26 →
The solenoid valves 32 and 33 are controlled so that the order is from the accumulator 29 to the compressor 25.

When YES is determined in the step 210, a target outlet temperature TAO to be blown into the vehicle compartment is calculated in the next step 215 based on the following equation (8).

[0053]

[Equation 8] TAO = Kset × Tset−Kr × Tr−Kam ×
Tam−Ks × Ts−C Here, Tset is a set temperature determined by the setting position of the temperature setting lever 48, Tr is the inside air temperature detected by the inside air temperature sensor 55, Tam is the outside air temperature detected by the outside air temperature sensor 56, And Ts are the amounts of solar radiation detected by the solar radiation sensor 57. Kset, Kr, Kam and Ks are gains, respectively, and C is a constant.

Then, in the next step 225, the target hot water temperature TWO is calculated based on the following equation (9).

[0055]

TWO = (TAO−Tin) / φ (V) + Tin where Tin is the air temperature on the suction side of the heater core 50, and in the present embodiment, the air temperature sensor 4
The detection value of 0 is substituted. Further, φ (V) is a temperature efficiency that varies depending on the air volume V of the fan 9, and the relationship between the temperature efficiency φ (V) and the air volume V is as shown in FIG. The relationship shown in FIG. 18 is stored in the ROM.

In the next step 230, the deviation Dn between the target hot water temperature TWO and the actual hot water temperature TW detected by the water temperature sensor 58 is calculated based on the following equation (10).

[0057]

Dn = TWO-TW After that, the processing after step 240 is performed. According to this embodiment, the compressor is controlled by controlling the inverter.
By controlling the rotation speed of the refrigerant water heat exchanger 4
9, the amount of hot water to be heated is controlled, and, consequently, the air heating capacity of the heater core 50 is controlled, and the temperature of air blown into the vehicle compartment is controlled.

In this embodiment as well, since the processing of steps 180 and 260 is performed, the behavior of the hot water temperature in the heating mode is almost the same as that in FIG. 13 in which the high pressure is replaced by the hot water temperature. . Next, a third embodiment of the present invention will be described with reference to FIGS. In the above embodiments, the predetermined target vehicle interior temperature,
Using fuzzy inference incorporating parameters corresponding to the deviation from the temperature of the air blown into the cabin, the target increase / decrease rotational speed Δfz
And the target increase / decrease rotational speed Δfz is corrected according to the set position of the air volume setting lever 45.However, in the fuzzy inference, a parameter relating to the set position of the air volume setting lever 45 is further incorporated. The target increase / decrease rotational speed Δf may be calculated using fuzzy inference. In this case, it goes without saying that the fuzzy inference is determined so that the target increase / decrease rotational speed Δf increases as the amount of air passing through the indoor heat exchanger increases.

The control processing of the inverter is as follows.
In steps 170 and 250, the air volume setting lever 45
After the target rotation speed Δf of the compressor 25 is calculated using fuzzy inference incorporating the parameters related to the set position of step (1), the processing of step 190 may be directly performed. Here, the processing in step 250 when the system according to the first embodiment is used is as follows.

First, CF1 obtained in FIG. 19A and FIG.
9 (b) and CF3 obtained in FIG. 19 (c)
Then, the input fitness CF is obtained based on the following mathematical formula 11, and Δf is calculated based on the mathematical formula 4 from the input fitness CF and the rule values in FIGS.

[0061]

## EQU11 ## CF = CF1.times.CF2.times.CF3 As described above, also in the present embodiment, not only the deviation between the predetermined target cabin temperature and the temperature of the air blown into the cabin, but also the air passing through the indoor heat exchanger. The target increase / decrease rotational speed Δf is also calculated according to the air flow to be performed. Therefore, regardless of the air flow passing through the indoor heat exchanger, the temperature of the air blown into the vehicle interior becomes
It always approaches the target vehicle interior temperature in an optimal state.

(Other Embodiments) In the first embodiment, in the heating mode, the target high pressure PCO is determined according to the set position of the temperature setting lever 48. However, the heating indoor heat exchanger is used. 23, the target air temperature TC immediately after passing
O (° C.) may be determined. In this case, a temperature sensor for detecting the air temperature immediately after passing through the heating indoor heat exchanger 23 is provided, and the deviation Dn is determined by the target temperature TCO
And the difference between the temperature and the detection value TC of the sensor.

In this embodiment, as shown in parentheses in FIG. 9, the controller sets the temperature setting lever 48 as shown in FIG.
When it is at the left end, the target temperature TCO is determined to be 30 (° C.), and when it is at the right end in FIG.
(° C). In each of the above embodiments, the deviation En (Dn) between the target value and the actual value and the deviation change rate Edot
Δf was obtained from (Ddot) using fuzzy inference,
Δf may be obtained using P control, PI control, PID control, or the like. Also, when fuzzy inference is used, the rule is not limited to the 5 × 5 rule, and a more detailed rule may be used, or a new rule may be used.

Each coefficient shown in FIG. 8 may have other values. The point is that the coefficient may be increased as the amount of air passing through the indoor heat exchanger increases.

[Brief description of the drawings]

FIG. 1 is an overall configuration diagram according to a first embodiment of the present invention.

FIG. 2 is a block diagram of a control system in the embodiment.

FIG. 3 is a front view of a control panel in the embodiment.

FIG. 4 is a control flowchart for an inverter in the embodiment.

FIG. 5 is a map showing a relationship between a temperature setting lever position and a target temperature TEO in the embodiment.

FIG. 6 is a membership function used in the cooling mode by the control device according to the embodiment.

[7] The control device is a fuzzy rule view table used in the cooling mode.

8 is a corresponding view table showing the relationship between the air volume setting lever position in the above embodiment the correction target decreasing rotational speed Delta] f.

FIG. 9 is a map showing a relationship between a temperature setting lever position and a target high pressure PCO (target temperature TCO) in the embodiment.

FIG. 10 is a membership function used by the control device in a heating mode.

11 is a fuzzy rule diagram table the control device used in the heating mode.

FIG. 12 (a) is a post-pass air temperature TE in the cooling mode.
And (b) is a graph showing the behavior of the compressor speed in the cooling mode.

13A is a graph showing a behavior of a high-pressure PC in a heating mode, and FIG. 13B is a graph showing a behavior of a compressor rotation speed in a heating mode.

FIG. 14 is an overall configuration diagram according to a second embodiment of the present invention.

FIG. 15 is a sectional view taken along the line AA of FIG. 14;

FIG. 16 is a block diagram of a control system according to the second embodiment.

FIG. 17 is a control flowchart for an inverter according to the second embodiment.

FIG. 18 is a graph showing a relationship between a temperature efficiency φ (V) and an air volume V.

FIG. 19 is a membership function used in a heating mode by the control device according to the third embodiment of the present invention.

FIG. 20 is a fuzzy rule view table used in the control apparatus heating mode in the third embodiment.

21 is a fuzzy rule view table used in the control apparatus heating mode in the third embodiment.

FIGS. 22 (a) and 22 (b) are graphs for the conventional case, in which (a) shows the behavior of the blow-off air temperature in the cooling mode, and (b) shows the behavior of the compressor speed in the cooling mode. Show.

FIGS. 23 (a) and 23 (b) are graphs for the conventional case, in which (a) shows the behavior of the outlet air temperature in the heating mode, and (b) shows the behavior of the compressor rotation speed in the heating mode. Show.

[Explanation of symbols]

2 ... duct (air passage), 4 ... blowing means, 22 ... cooling indoor heat exchanger (evaporator), 23 ... heating indoor heat exchanger (condenser), 24 ... refrigeration cycle, 25 ... compressor, 26
... outdoor heat exchanger (condenser, evaporator), 27 ... cooling decompression device (decompression means), 28 ... heating decompression device (decompression means), 37 ... electric motor (drive means), 39 ... control device, 40 ... Air temperature sensor after passing (cooling degree detecting means), 42 ... High pressure sensor (high pressure detecting means), 48 ...
Temperature setting lever (temperature setting means), 49: refrigerant water heat exchanger, 49c: refrigerant passage (condenser), 50: heater core (hot water type heat exchanger), 54: hot water circuit, 58: water temperature sensor (hot water temperature detection) means).

──────────────────────────────────────────────────続 き Continuation of front page (72) Inventor Akira Isaji 1-1-1, Showa-cho, Kariya-shi, Aichi Japan Inside Denso Co., Ltd. (56) References JP-A-62-228830 (JP, A) JP-A-6-228 262936 (JP, A) JP-A-8-216662 (JP, A) (58) Fields investigated (Int. Cl. ⁷ , DB name) F24F 11/02 102

Claims (6)

(57) [Claims] An air flow generating means for generating an air flow; an air passage for guiding air generated by the air blowing means into a room; and a refrigerant when driven by a driving means. (25) that sucks, compresses, and discharges the
5) a condenser (26) for condensing the refrigerant from the condenser (26), a decompression means (27) for decompressing the refrigerant from the condenser (26), and evaporating the refrigerant from the decompression means (27) and the air passage ( 2) Evaporator (22) provided in
A refrigeration cycle (24) provided with: a deviation between a predetermined target indoor temperature and a temperature of air blown into the room ;
And the compressor (25) according to the rate of change of the deviation.
Target rotation speed determining means (steps 140 to 190) for determining the target rotation speed, and drive control means (step 200) for controlling the driving means (37) so that the actual compressor rotation speed becomes the target rotation speed. Control device (3)
9), and is configured to perform indoor cooling by blowing air that has passed through the evaporator (22) into the room, and as the amount of air passing through the evaporator (22) increases, , The target rotational speed determining means (steps 140 to 19)
0) air conditioning system, characterized in that to increase the target speed determined by the. A temperature setting means (48) operated by an air-conditioning operator; and a cooling degree detecting means (40) for detecting a degree of air cooling in the evaporator (22) . By the temperature setting means (48)
This is a set temperature, and the temperature of the air blown into the room is sent to the evaporator (22).
The air conditioner according to claim 1, wherein the temperature is a temperature indicating a degree of air cooling . 3. An air blowing means (4) for generating an air flow, an air passage (2) for guiding air generated by the air blowing means (4) into a room, and a refrigerant when driven by a driving means (37). (25) that sucks, compresses, and discharges the
5) a condenser (23) provided in the air passage (2) while condensing the refrigerant from the condenser (2);
3) a decompression means (28) for decompressing the refrigerant from the evaporator (2) for evaporating the refrigerant from the decompression means (28).
6) a refrigeration cycle (24) provided with: a deviation between a predetermined target indoor temperature and a temperature of air blown into the room ;
And the compressor (25) according to the rate of change of the deviation.
Target rotation speed determining means (steps 220 to 260, 190) for determining the target rotation speed, and drive control means (37) for controlling the driving means (37) so that the actual compressor rotation speed becomes the target rotation speed. step 200) the control unit and a (39) comprises a passage by blowing air having passed through the condenser (23) to the chamber, is configured to perform the room heating, the condenser (23) The target rotation speed determining means (steps 220 to 26)
0, 190) to increase the target rotational speed.
Air conditioner characterized by doing. 4. An air flow generating means (4) for generating an air flow, and an air flow guiding the air generated by the air blowing means (4) into a room.
The refrigerant is absorbed when driven by the path (2) and the driving means (37).
Compressor (25) for input, compression and discharge,
5) condensing the refrigerant from
The condenser (23) provided in (2), the condenser (2)
Pressure reducing means (28) for reducing the pressure of the refrigerant from 3), and
Evaporator (2) for evaporating the refrigerant from the pressure reducing means (28)
6) a refrigeration cycle (24), a temperature setting means (48) operated by an air conditioning driver, a high pressure detection means (42) for detecting a high pressure of the refrigeration cycle (24), and the temperature It is determined according to the setting position of the setting means (48).
The target high pressure and the high pressure detection means (42) .
Deviation from the detected high pressure and the change in this deviation
Target rotation speed determining means (steps 220 to 260, 19 ) for determining a target rotation speed of the compressor (25) according to the rate.
0), and the actual compressor speed becomes the target speed.
Control means for controlling the driving means (37) as described above
(Step 200) and a control device (39).
The air passing through the condenser (23) is blown into the room.
, So that the room is heated, and as the amount of air passing through the condenser (23) increases,
The target rotation speed determining means (steps 220 to 26)
0, 190) to increase the target rotational speed.
Air conditioner characterized by doing. 5. An air blowing means (4) for generating an air flow, an air passage (2) for guiding air generated by the air blowing means (4) into a room, and a refrigerant when driven by a driving means (37). (25) that sucks, compresses, and discharges the
5) a condenser (49c) for condensing the refrigerant from the condenser, and a pressure reducing means (2) for decompressing the refrigerant from the condenser (49c).
8) and a refrigeration cycle (24) provided with an evaporator (26) for evaporating the refrigerant from the decompression means (28), and heats the refrigerant in the condenser (49c) and the hot water flowing inside itself. A refrigerant water heat exchanger (49) to be exchanged, and a hot water heat exchanger (50) provided in the air passage (2) while hot water from the refrigerant water heat exchanger (49) flows therein. A hot water circuit (54), a deviation between a predetermined target indoor temperature and a temperature of air blown into the room ,
And the compressor (25) according to the rate of change of the deviation.
Target rotation speed determining means (steps 215 to 260, 190) for determining the target rotation speed, and drive control means (37) for controlling the driving means (37) so that the actual compressor rotation speed becomes the target rotation speed. step 200) the control unit and a (39) comprising, said by blowing hot water type heat exchanger of air passing through the (50) to the chamber, is configured to perform the room heating
The target rotation speed determining means (steps 215 to 215) as the amount of air passing through the hot water heat exchanger (50) increases.
Air-conditioning system, characterized in that the increase the target speed determined by 260,190). 6. A temperature setting means (48) operated by an air-conditioning driver; and a hot water temperature detecting means (58) for detecting a temperature of hot water flowing into the hot water heat exchanger (50). The target room temperature is determined by the temperature setting means (48).
The set target hot water temperature, and the temperature of the air blown into the room is determined by the hot water heat exchanger (5).
6. The air conditioner according to claim 5, wherein the temperature is the temperature of the hot water flowing into the inside of 0).